Rotary pump of the single rotor type



Sept. 24, 194-0. 5 M STALEY ROTARY PUMP OF THE SINGLE ROTOR TYPE Filed Jan. 24.v 1939 5 Sheets-Sheet l FIQS INVENTOR BENJAMIN M7 STALEY ATTORNEY p 4,1940; B. M. STALEY 2,216,053

ROTARY PUMP OF THE SINGLE ROTOR TYPE Filed Jan. 24, 1959 5 Sheds-Sheet 2 20 g Qfl g, W 6:

F/GJP.

I INVENTOR BENJAMIN M- STALEY V I BY ATTORNEY Sept. 24, 1940. a M. STALEY I ROTARY PUMP OF THE SINGLE ROTOR TYPE Filed Jan. 24, 1939 5 Sheets-Sheet 5 INVENTOR BENJAMIN M STALEY ATTORNEY Patented Sept. 24, 1940 UNITED STATES 2,216.05: LOTABY runs or run SINGLE no'roa ma Benjamin Maxwell Staley, Oil City, Pa., assignor to National Transit Pump a Machine 00., Oil City, Pa... a corporation of Fennsylvania Application January 2 4, 1939, Serial No: 252,571

4Clainis.

This invention relates to a rotary pump of the type having a single rotor mounted within a body or casing having'a bore which is concentric with and larger in diameter than said rotor: and a liner within said bore in fixed relation thereto, with its outer diameter concentric with said bore, and its inner diameter 'excentric thereto. The difierence between the diameter of the bore of the liner and the. peripheral diameter of the rotor is substantially the displacement per revolution of this pump.

The objects of this invention are the attainment of the following points of superiority:

A construction wherein and whereby the impeller m or rotor vanes during the interval of their discharge travel are actuated into operative leaktight contact with the adjacent face of the liner by the combined action of' centrifugal iforce together with the delivery pressure,.under which the pump is operating, and at thesuction interval by centrifugal force only. I The discharge through the outlet opening of all the liquid contained in the successive sockets 25 interval of their travel.

The cushioning of the blades during the discharge interval of operation against high pressure. An emergencypressure relief whereby, in case fluid within the pump casing without any further increase in headpressure, the degree of said maximum pressure being determined and regulated at will. liner so constructed as to.cause an equal year throughout the entire length of the rotor vanes. Means whereby fluid pressure is prevented from taking place withinthe stufllng boxes of the rotor shaft.

The construction whereby said objects are attained is clearly; illustrated in the accompanying'drawingsconsfiting of the following views:

Fig. 1 is .an end view of the rotor organization with a portion 01' the rotor and one of the-vanes ,carried thereby, shown in section, together with the liner, which latter is also shown in section.

' Fig. 2 is a diametrical assembly-section through.

the rotor," the liner and the side-plates of this 50 assembly, the shaft being shown in elevation.

Fig. 3 is a plane-view of the inner fac'eof the liner as it would appear if sawed transversely at r or about the point A Fig. 1, and straightened out; said liner being shown in section in Fig. 1

55 Jon theline bc of this Fig. 3.

formed between the vanes in the discharge.

an abnormal discharge pressure is accidentally set up, said relief will cause a circulation of Fig. 4 is a side elevation of the laminated face ofarotor vane;

Fig. 5 is a transverse section of said vane;

Fig. 6 is an end view of said vane.

Fig. '7 is a central, vertical, transverse section oii one form of casing in which the foregoing details are assembled: the liner and shaft being shown also in section and the rotor in end elevation: A pressure-relief valve also appears in central, vertical section in this view.

Fig. 8 illustrates the upper portion of thesame -iorm of casing as shown in Fig. 7 with a some what modified pressure-relief valve; the rotor, .its vanes and the liner being shown in transverse section. v

Fig. 9 is a vertical, central, longitudinal section (para lel with the axial line of the drive shaft) of one form of casing which may be used with the details previously mentioned, and as illustrated, in Fig. 1.

Fig. 10 is an end view of the lower half of the casing-head shown in Fig. 9. v

Fig. 11 is an illustration of another form of casing organization in which the identical ele- 'ments previously mentioned may be assembled. The body of this casing shown in Fig. 11 is sub stantially identical with the body shown in Figs. 7 and 9, but the types of elongatedheads here shown, are preferably, the forms used in pumps of large capacity, especially so upon account of the greater length and rigidity of shaft bearings said modified forms of casing, as illustrated in Figs. 9 and 11, -are shown for the purpose of indicating the .various types and forms in which my improved 'rotor'and liner are embodied, in pumps which vary in size and capacity;

' The construction illustrated in said drawings and the operation of the resulting pump, is substantially as follows:

A body or casing l is provided with a bore or chamber 2; within said bore is inserted a liner 3, which is secured in said bore against rotation by any suitable means such as a key, which seats in the keyway [of Fig. '7 and a corresponding key-way in the pump casing; said liner is of such outside diameter as to form a snug fit in the boreof said casing; the bore of the liner is excentric, relatively to the periphery or outside diameter thereof; this liner is provided with a plurality of inlet or suction ports or passages as 5, -.'i,.5, and a number of discharge ports or passages as 6, 6 as shown in Fig. 1; said inlet and discharge ports being staggered with respect to each othertransversely of the liner, as showr in Fig. 3, whereby an equality of wear upon the outer contact edge of the rotor vanes 1, is insured throughout their entire length; this equality of wear is also caused to take place upon the adjacent face of the liner. The combined area of each set of ports 5, and B exceedsthe area of the suction or inlet and the discharge passage respectively. The rotor 8 is mounted upon, keyed to and driven by the shaft 9. It is also to be noticed that the longitudinal axes of the passages or ports 5 and 6 are arranged at right angles to the longitudinal axis of the liner and rotor while the opposed side edges of each of these passages are slightly tapered toward each other in the direction of rotation of the rotor.

' Said rotor is provided with a plurality of vane pockets H), which are disposed radially therein and extend longitudinally thereof; the fit of said vanes, 1 within said pockets is such that centrifugal force, as the rotor revolves, actuates said vanes outwardly throughout the suction portion of their travel; the liner, throughout the .dis-

charge, interval, actuates said vanes inwardly: Let it be noted, however, that, in order to insure certainty and sufficiency of functional performance of said blades, means acting in conjunction with said centrifugal force is provided in the form of radially-disposed sockets or grooves H, which are formed in any suitable manner in the face of the leading or advancing wall of said pockets and extend inwardly beyond the bottom of said pockets l|l,as clearly indicated in several figures of the drawings,see Figs. 2, 8 and 11, and as the rotor revolves, the discharge pressure of the actuated fluid causes portions of it to enter said sockets, and fill the space at the bottom of said blades and to thereby exert full, discharge, outwardly-directed pressure thereon, whereby a reverse leakage of actuated fluid is prevented, and a degree of efl'iciency beyond that known to applicant in any other type of rotary pump, is attained.

Attention is directed to the coaction existing between the circumferential spacing of the inlet and discharge passages or ports 5 and 6 in the liner and the relief sockets I l in the vane pockets In. As shown in Figs. 3 and 7 the space or land 5 between the rear edges of the inlet passages 5 and the front edges of the discharge passages 6 corresponds substantially to the width of each of the sliding vanes I plus half of the width of each of the relief sockets I| while the space or land 6' between the front edges of the inlet passages 5 and the rear edges of the discharge passages 6 corresponds to the distance from the trailing edges of one sliding vane 1 to the leading edge of the following sliding vane when the sliding vane is in contact with the liner. As a result of the relation between the spaces 5' and 6"with the sockets I, the sockets maintain communication with the discharge passages in the liner until the vanes 1 reach the inner ends of the pockets l0.

By reference to Figs. 7 and 8 it will be noted how a novel form of automatic pressure relief is provided; this provision being as follows:

In the Fig. 8 form of this relief organization, the discharge chamber of the pump is extended laterally, to form a relief,chamber |2;' one wall l2 of which is a dividing wall between, and is common to, said relief chamber and the inlet chamber; the upper wall of this chamber is provided with an outlet-port I3, which is equipped with an outlet-valve I4 whereby communication with the suction chamber I5 of the casing is provided. Said valve I4 is normally retained adapted for the seating of the lower end of another compression spring l8; upon the upper end of said spring l8-is mounted another springstructure which consists of a socket, or tubular element "l9, provided at its upper end with a horizontally-extending flange 20, and this flange forms the supporting feature for said tubular element l9; within and seating upon an inwardlyextending annular flange in the bottom of said tubular element I9, is a third compression spring 2|; 9. disc 22 is seated upon the upper end of said last-mentioned spring 2|.

Said spring structure extends upwardly into a tubular casing 23 which is suitably secured at its lower end to the pump body. Said casing 23 is closed at its upper end, and a vertically-extending, compression screw 24 extends through the upper wall thereof and bears upon the disc 22. The function of this multiple spring and compression structure is, to hold said valve 4 to its seat at various and selective degrees of pressure, which are determined by means of said regulating member 24. "In the position in which said member 24 appears in the drawings, only a comparativelylow degree of discharge pressure will be had,s'ince it is necessary to compress only the lightest spring 2| in order to open valve l4. If a higher pressure is desired, a full compression of spring 20 must be had whereupon spring I!) is caused to function through its possible range; when the limit of compression of this spring I! is reached, spring 2| will be brought into action and will operate throughout the range of its compressibility. A detailed description of the spring structure illustrated in Fig. '7 is deemed unnecessa y. since it is clearly apparent that the mode of operation thereof is substantially the same as the Fig. 8 form, but its range of pressure as compared thereto will be reduced by about one third: It is also evident that an increase of range may be had by the addition of other or heavier springs.

When the degree of pressure for which said relief valve isset is reached saidpre'ssure of the pumped fluid,'opens said valve and a portion of the pumped fluid passes therethrough, as indicated by the dotted arrows in Fig. 8, the result being that a portion of the fluid is circulated within the pump casing instead of being discharged therefrom in the usual manner. Tubular casings, such as H and 20 are employed for the purpose of preventing intermeshing of the coils of the nested springs, or any buckling of the individual springs, such as would prevent the free action of same, at any stage of their action,

is such as to present low frictional resistance to the contacting face of the rotor pockets thus =facilitating the outward and inward movements of said vanes.

" In respect to the form and detail-construction of the pump casing, ;modiflcations thereof are within the inventive scope of the illustrations forms of easing organization both of which em-- given: Figs. 8 and 11 clearly show two differing body the operative details shown in Figs. 1 to 6 of Sheet One; these forms differ in respect to the construction of the combined head and shaftbearing members, which may be selectively used, as the capacity and purpose of the pump may require- Both formsof casing heads shown in Fig. 9 and Fig. 11 show means for preventing the access of the pumped liquid, from the pressure side of the rotor chamber, to the bearings of the rotor shaft and the stumng boxes thereof;it being Well-known that such access of fluid to the shaft bearings of rotary pumps seriously interferes with their proper lubrication, and causes heating and rapid wear. This object is accomplished in the manner illustrated in Figs. 2, and 11, in each of which are shown a channel 21 extending downwardly from the shaft and having communication with the suction area of the rotor chamber. In Fig. 9, said object is attained in the following way: any liquid which enters the shaft bearings, bleeds therefrom through the openings 28, into the pockets 29;

. of the liner at the top of the pump cylinder, and

is thus readily removed therefrom.

The body member, as illustrated in the drawings, may be of the same type in all sizes of pumps, and the differing forms of ends, as shown in Figs. 9 and 10, may be interchangeably used with said body, but generally, the Fig. 9 heads are used upon the smaller sizes of pumps and the Fig. 11 formof heads are used upon pumps of large capacity.

It may also be readily noted thatthe open type of head, as 32 or 33, may be used upon both sides of the body if desired.

I claim the following:

1. A rotary pump including a casing provided with an inlet passage and with a'discharge passage'and a rotor chamber positioned intermediate said passages, a liner removably fixed in the chamber and provided with a series of inlet passages and a series of discharge passages circumferentially spaced from each other and respectively registering with inlet and discharge Passages in the casing, a rotor operating within'the liner and eccentrically thereof and provided with a series of radially disposed pockets, vanes slidable radially in the pockets and operating-against the inner face of the liner,and the Walls of the pockets adjacent the leading edges of the vanes being provided with'a series of inwardly extending sockets which terminate. beyond the inner ends of the pockets, the circumferential spacing between the inlet and discharge passages in the liner beingso related to the sockets that said sockets maintain communication with the discharge passages in the liner until the vanes reach the inner ends of the pockets.

2. A rotary pumpas claimed in claim 1, in

I which the space between the rear edges of the inlet passages in the liner and the front edges of the discharge passages thereof corresponds substantially to the width of each of the sliding vanes plus half of the width of each of the relief sockets.

3. A rotary pump as claimed in claim 1, in which the space between the front edges of the inlet passages and the rear edges of the discharge passages corresponds substantially to the distance from the trailing edge of one sliding vane to the leading edge of the following sliding vane when the sliding vane is.in contact with the liner.

4. In a rotary pump of the type having a rotor having radially slidable vanes, a cylindrical liner surrounding the rotor and in contact with the rotation of the rotor.

BENJAMIN MAXWELL STALEY. 

